US3977503A - Clutch - Google Patents

Clutch Download PDF

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Publication number
US3977503A
US3977503A US05/598,313 US59831375A US3977503A US 3977503 A US3977503 A US 3977503A US 59831375 A US59831375 A US 59831375A US 3977503 A US3977503 A US 3977503A
Authority
US
United States
Prior art keywords
drive member
members
drive
gear
combination
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/598,313
Other languages
English (en)
Inventor
John W. Hurst
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Old Carco LLC
Original Assignee
Chrysler Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Chrysler Corp filed Critical Chrysler Corp
Priority to US05/598,313 priority Critical patent/US3977503A/en
Priority to NZ180752A priority patent/NZ180752A/xx
Priority to CA76251685A priority patent/CA1048426A/en
Priority to AU13725/76A priority patent/AU503227B2/en
Priority to IT23131/76A priority patent/IT1066864B/it
Priority to SE7605285A priority patent/SE7605285L/xx
Priority to GB19500/76A priority patent/GB1495919A/en
Priority to BR7603477A priority patent/BR7603477A/pt
Priority to JP51083048A priority patent/JPS5224660A/ja
Priority to DE19762633056 priority patent/DE2633056A1/de
Priority to FR7622431A priority patent/FR2319051A1/fr
Priority to FI762101A priority patent/FI762101A7/fi
Priority to NO762565A priority patent/NO147002C/no
Priority to ES450087A priority patent/ES450087A1/es
Application granted granted Critical
Publication of US3977503A publication Critical patent/US3977503A/en
Assigned to FIDELITY UNION TRUST COMPANY, TRUSTEE reassignment FIDELITY UNION TRUST COMPANY, TRUSTEE MORTGAGE (SEE DOCUMENT FOR DETAILS). Assignors: CHRYSLER CORPORATION
Assigned to CHRYSLER CORPORATION reassignment CHRYSLER CORPORATION ASSIGNORS HEREBY REASSIGN, TRANSFER AND RELINQUISH THEIR ENTIRE INTEREST UNDER SAID INVENTIONS AND RELEASE THEIR SECURITY INTEREST. (SEE DOCUMENT FOR DETAILS). Assignors: ARNEBECK, WILLIAM, INDIVIDUAL TRUSTEE, FIDELITY UNION BANK
Assigned to CHRYSLER CORPORATION reassignment CHRYSLER CORPORATION PARTES REASSIGN, TRANSFER AND RELINQUISH THEIR ENTIRE INTEREST UNDER SAID PATENTS ALSO RELEASE THEIR SECURITY INTEREST. (SEE RECORD FOR DETAIL) Assignors: MANUFACTURERS NATIONAL BANK OF DETROIL (CORPORATE TRUSTEE) AND BLACK DONALD E., (INDIVIDUAL TRUSTEE)
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/14—Gearings for reversal only
    • F16H3/145—Gearings for reversal only with a pair of coaxial bevel gears, rotatable in opposite directions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/24—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches
    • F16D13/26—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches in which the or each axially-movable member is pressed exclusively against an axially-located member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/04—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways with a shaft carrying a number of rotatable transmission members, e.g. gears, each of which can be connected to the shaft by a clutching member or members between the shaft and the hub of the transmission member

Definitions

  • the invention relates to drive couplings and more particularly to clutches.
  • it comprises a cone clutch or reversing transmission for inboard-outboard marine drive units such as the type shown in U.S. Pat. No. 3,893,407 for example or for outboard motors and other marine drive devices.
  • corresponding radially distributed helical camming surfaces carried on abutting end portions of a gear and an axially moveable female cone are in axial overlapping relationship whereby the camming surfaces therebetween are able to drivingly engage each other when the gear or the female cone is rotated.
  • female cone rotation is initiated by axial movement thereof into engagement with a rotatable male cone.
  • driving engagement of the axially overlapping helical cam surfaces of the abutting female cone and gear occurs whereby the gear is rotated to provide rotation to output means.
  • the camming surfaces coact to urge the female cone into more positive engagement with the male cone.
  • FIG. 1 is a side elevational view in section of a reversing clutch embodying various features of the invention. It is particularly designed for use in an inboard-outboard marine drive unit.
  • FIG. 2 is a fragmentary plan view of an upper portion of FIG. 1 taken from line 2--2 in FIG. 1.
  • FIG. 3 is a fragmentary sectional view taken along line 3--3 of FIG. 1.
  • FIG. 4 is a fragmentary sectional view taken along line 4--4 of FIG. 1.
  • FIG. 5 is a fragmentary sectional view taken along line 5--5 of FIG. 4.
  • FIG. 6 is a fragmentary sectional view taken along line 6--6 of FIG. 1.
  • FIG. 7 is an exploded detail perspective view of a part of a female cone and gear showing the helical surfaces on abutting end portions of the members.
  • FIG. 8 is a fragmentary sectional view of both the helical surfaces of a gear and female cone in driving engagement and the conical surfaces of female and male cones in driving engagement.
  • FIG. 9 is an alternate embodiment of a clutch embodying features of the invention and also showing both the helical surfaces of the female cones and gears in a neutral condition and the conical surfaces of the female and male cones in a neutral condition.
  • FIG. 1 shows a reversing clutch generally designated 10, such as may be included in the outboard power leg of an inboard-outboard marine propulsion unit or stern drive having an upper housing portion 11 (shown fragmentarily) on an outboard power leg (not shown).
  • a reversing clutch generally designated 10
  • an input shaft 12 is adapted as at 14 for connection to the output shaft (not shown) of an inboard mounted engine whereby input shaft 12 may be rotated to drive a propeller (not shown) carried on a lower portion of the outboard power leg.
  • Input shaft 12 carries various clutch members which coact in combination to provide a reversible rotary output to an output shaft 16, which drives the propeller on the power leg.
  • first drive member or male cone member 18 Fixed to shaft 12 and rotatable therewith is a first drive member or male cone member 18 having opposing frusto-conical convex faces 18a and 18b.
  • shaft 12 Toward each side i.e., on opposite sides, of male cone member 18, shaft 12 carries second and third drive members or female cone members 20 and 22 having frusto-conical concave interior rim portions or faces 20a and 22a, respectively.
  • Female cone members 20 and 22 are both mounted on shaft 12 so that they rotate freely thereon and also be axially moveable thereon over a range of travel toward and away from male cone member 18.
  • This arrangement provides a cone clutch wherein the second and third drive members are oppositely coned female clutch members and the first drive member is a mating coned male clutch member.
  • this one is preferably carried inside a housing 11 which contains a substantial amount of oil.
  • the clutch members may be partially or wholly immersed in lubricating oil. It is therefore preferred that either the rim portions of 20a and 22a or the face portions 18a and 18b of member 18 (as shown in FIG. 1) be provided with a plurality of small grooves 24 arranged to wipe oil from therebetween when any of the surface portions of these members come into mutual contact during operation of the clutch.
  • This may be further understood as to purpose and arrangement by having reference to the teaching set forth in the Society of Automotive Engineers paper No. 311B entitled Automatic Transmission Friction Elements by Froslie, Milek and Smith, which was delivered at the SAE meeting of Jan. 9-13, 1964, with particular reference to pp. 2-3 thereof.
  • each of the bushings includes an extending portion 26a and 28a respectively, best illustrated in FIG. 7 which provide for stable sliding movement of each female cone on shaft 12.
  • Each female cone member 20 and 22 is provided with means generally designated 30 (FIGS. 2 and 3) for selectively moving the female cone into and out of contact with the male cone member 18.
  • means 30 will take the form of a pair of arcuate fork members 32 and 34 slidably mounted on a rail 36.
  • Each of the fork members is connected to one of the female cones.
  • a preferred arrangement for this connection is shown in the drawings and includes an annular member 38 fitted to each of the female cones as by the screw threads on the extending portion of the cone as shown in FIGS. 1 and 7.
  • Each member 38 carries a ring 40 having an annular groove 42. Ring 40 is positioned between two annularly distributed sets of needle bearings indicated at 44 which facilitate rotation of ring 40 relative to its corresponding female cone member.
  • Means 30 will preferably be designed to provide simultaneous movement of the forks and female cone members as by tying the two forks together for simultaneous movement through a sleeve 41 which slides on rail 36.
  • the forks may be attached to the sleeve by bolts as shown in FIGS. 2 and 3.
  • both female cones may be readily placed in a neutral condition relative to male cone member 18, as shown in FIGS. 1 and 9.
  • one or the other of the female cones may be selectively brought into contact with the male cone member to provide a forward or reverse driving condition.
  • a driving condition is illustrated in FIG. 8 which shows female cone 20 contacting male cone 18 to provide a forward condition (arbitrarily selected) for output shaft 16.
  • the rotation of output shaft 16 is provided by interaction between three gears.
  • Two of the gears 46 and 48 are carried on input shaft 12 while the third gear 50 is placed between the first two gears so as to constantly intermesh with them.
  • Gears 46 and 48 are axially fixed on shaft 12 but freely rotatable thereon whereby rotation of either gear causes rotation of gear 50 and hence rotation of output shaft 16. Minor axial movement of the gears 46 and 48 may occur on shaft 12. For example, movement of 0.010 inch or less has been experienced with these gears in operation without any malfunction. It can be said that the gears are substantially axially fixed on the shaft.
  • gears 46 and 48 are driven by the respective female cone to which they are adjacent and abut.
  • Each gear is placed on shaft 12 adjacent a side of the respective female cone which is opposite the female cone side to which the male cone is adjacent.
  • each female cone is positioned between the male cone and one of the rotatable gears 46 or 48.
  • Interconnection for coaction between the female cone members and their adjacent abutting gear is constantly provided by sets of a plurality of complementary radially distributed overlapping helical camming surfaces, generally designated at 52 and 54 (best seen in FIGS. 7, 8 and 9) which are carried on adjacent abutting portions of the female cone-gear pairs 20-46 and 22-48 respectively.
  • the helical surfaces are formed on adjacent portions of the female cone-gear pairs as shown in the form of cylindrical abutting end portions or side portions thereof, 52 and 54 respectively.
  • the spiral direction of the helical surfaces is in an opposite direction for each cone-gear pair 20-46 and 22-48, i.e., the helical surfaces are "opposite handed" to provide proper coaction for opposite directions of rotation of output shaft 16 depending on which cone-gear pair is driving gear 50 and is being driven in turn by male cone 18.
  • the helical surfaces may be symmetrical and alternate surfaces may be used to obtain "opposite handedness”.
  • helical surfaces 52a on the female cone-gear pair 20-46 would coact to drive gear 50 through gear 46; rotation of gear 46 and female cone 20 being in the direction indicated by the arrows.
  • the drive action will be through helical surfaces 54a.
  • the helical surfaces 52a of cone-gear pair 20-46 spiral in one direction for engagement between the cone-pair 20-46 rotate on shaft 12 when cone 20 drives gear 46 or when gear 46 idles and drives cone 20; see FIGS. 7 and 8.
  • the helical surfaces 54a of cone-gear pair 22-48 spiral in a second direction for engagement between those members.
  • each cone-gear pair Since the helical surfaces of each cone-gear pair are constantly overlapping over the entire extent of the axial travel of each female cone, constant driving engagement between each female cone-gear pair is readily provided when the female cone is brought into contact with the rotating male cone 18. Interaction of the helical surfaces upon rotation also provides a positive force which urges the female cone against the male cone to improve the coupling action therebetween.
  • thrust washer 56 and 58 Each of the gears 46 and 48 rests against a thrust washer 56 and 58, respectively, on shaft 12.
  • the thrust washers in turn rest against a set of bearings and races generally indicated at 60 and 62.
  • the thrust washers are fixed to shaft 12 and rotate with it.
  • thrust washer 58 which is at the end of shaft 12, is especially adapted to cause circulation of the lubricating oil in which the clutch is operated inside housing 11.
  • the oil is circulated to various clutch members on the shaft by the thrust washer. This is accomplished by providing thrust washer 58 with paddle-like extensions 64 which, upon rotation of washer 58, push the oil rearwardly of the end of shaft 12 through conduits 66 in housing 11 and into cavity 68 as indicated by the arrows in FIG. 1.
  • Shaft 12 is provided longitudinally with a hollow center portion 70 and also with a plurality of spaced radiating conduits 72 extending therefrom to the outside surface of the shaft for allowing oil to flow from cavity 68 through hollow portion 70 of shaft 12 and then outwardly to various locations along the shaft to the clutch members as indicated by the arrows in FIG. 1.
  • Various clutch members may also be provided with oil passages 74 as are shown in FIGS. 4 and 5 on thrust washer 58 by way of example.
  • the clutch described above operates as follows.
  • the rotary output of an engine is normally in one given direction.
  • rotation of shaft 12 will be unidirectional, for example, in the counter-clockwise direction indicated by the arrow in FIG. 1. and viewed from the aft end of the shaft, i.e., the right handed end shown in FIG. 1. All references to rotation are made from this vantage point in the specification.
  • male cone 18 will be unidirectional in rotation also and will rotate with input shaft 12 in the same direction.
  • Axial movement of female cone 20 into contact with male cone 18 as shown in FIG. 8 causes rotation of gear 46 through the engaged overlapping helical surfaces 52a and rotation of meshing gear 50 and output shaft 16 in a first rotary direction.
  • gear 50 causes gear 48 and female cone 22 to idle on shaft 12 and rotates in an opposite direction.
  • the clutch members are arranged vertically on the output shaft 16 and the intermeshing gear 50 is placed on the input shaft 12 to function as an input gear which drives the two gears 46 and 48 on output shaft 16.
  • Axially movable female cone members 20 and 22 are rotated through sets of helical surfaces 52 and 54, respectively, and are selectively engageable with male cone member 18, which is fixed to shaft 16, to drive it in opposite rotary directions and hence to provide reverse rotation to output shaft 16.
  • a neutral condition may be obtained as before by positioning both female cones away from the male cone.
  • the driving helical surfaces of both sets are arranged in the same spiral direction rather than being "opposite handed" as in the other embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Structure Of Transmissions (AREA)
  • General Details Of Gearings (AREA)
  • Paper (AREA)
  • Manufacturing Of Electric Cables (AREA)
  • Earth Drilling (AREA)
  • Gear Transmission (AREA)
US05/598,313 1975-07-23 1975-07-23 Clutch Expired - Lifetime US3977503A (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US05/598,313 US3977503A (en) 1975-07-23 1975-07-23 Clutch
NZ180752A NZ180752A (en) 1975-07-23 1976-04-30 Two-position gear mechanism
CA76251685A CA1048426A (en) 1975-07-23 1976-05-03 Clutch
AU13725/76A AU503227B2 (en) 1975-07-23 1976-05-06 Clutch
IT23131/76A IT1066864B (it) 1975-07-23 1976-05-10 Giunti di accoppiamento di trasmissione in particolare innesti
SE7605285A SE7605285L (sv) 1975-07-23 1976-05-10 Koppling
GB19500/76A GB1495919A (en) 1975-07-23 1976-05-12 Drive clutch assembly
BR7603477A BR7603477A (pt) 1975-07-23 1976-05-31 Embreagem
JP51083048A JPS5224660A (en) 1975-07-23 1976-07-14 Clutch
DE19762633056 DE2633056A1 (de) 1975-07-23 1976-07-22 Kupplung
FR7622431A FR2319051A1 (fr) 1975-07-23 1976-07-22 Embrayage
FI762101A FI762101A7 (en:Method) 1975-07-23 1976-07-22
NO762565A NO147002C (no) 1975-07-23 1976-07-22 Anordning ved kobling.
ES450087A ES450087A1 (es) 1975-07-23 1976-07-23 Perfeccionamientos en embragues reversibles.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US05/598,313 US3977503A (en) 1975-07-23 1975-07-23 Clutch

Publications (1)

Publication Number Publication Date
US3977503A true US3977503A (en) 1976-08-31

Family

ID=24395068

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/598,313 Expired - Lifetime US3977503A (en) 1975-07-23 1975-07-23 Clutch

Country Status (14)

Country Link
US (1) US3977503A (en:Method)
JP (1) JPS5224660A (en:Method)
AU (1) AU503227B2 (en:Method)
BR (1) BR7603477A (en:Method)
CA (1) CA1048426A (en:Method)
DE (1) DE2633056A1 (en:Method)
ES (1) ES450087A1 (en:Method)
FI (1) FI762101A7 (en:Method)
FR (1) FR2319051A1 (en:Method)
GB (1) GB1495919A (en:Method)
IT (1) IT1066864B (en:Method)
NO (1) NO147002C (en:Method)
NZ (1) NZ180752A (en:Method)
SE (1) SE7605285L (en:Method)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022308A (en) * 1976-04-23 1977-05-10 Chrysler Corporation Drive coupling and clutches
US4051934A (en) * 1976-04-23 1977-10-04 Chrysler Corporation Bidirectional drive coupling
US4138006A (en) * 1977-10-31 1979-02-06 Paragon Gears Incorporated Power transmission of the interleaved, multiple friction plate clutch type
US4189038A (en) * 1977-07-18 1980-02-19 Chrysler Corporation Drive coupling and clutches
US4244454A (en) * 1979-04-30 1981-01-13 Brunswick Corporation Cone clutch
US5149308A (en) * 1988-08-22 1992-09-22 Kubota, Ltd. Transmission
US20120066975A1 (en) * 2010-08-05 2012-03-22 Asmo Co., Ltd. Clutch, motor and vehicle door opening/closing device
US20140038478A1 (en) * 2012-01-24 2014-02-06 Arkmos Engineering, LLC Outboard Marine Drive
US9919783B1 (en) 2016-10-31 2018-03-20 Brunswick Corporation Transmission housing for mounting a transmission between a driveshaft housing and a lower gearcase in an outboard motor
US9964210B1 (en) 2016-10-31 2018-05-08 Brunswick Corporation Transmission actuator for an outboard motor having a planetary transmission
US10124874B1 (en) 2015-01-26 2018-11-13 Brunswick Corporation Systems and methods for controlling planetary transmission arrangements for marine propulsion devices
US10239598B2 (en) 2016-10-31 2019-03-26 Brunswick Corporation Cooling system for an outboard motor having a hydraulic shift mechanism
US10315747B1 (en) 2016-11-09 2019-06-11 Brunswick Corporation Outboard motors having transmissions with laterally offset input and output driveshafts
US10502312B1 (en) 2016-10-31 2019-12-10 Brunswick Corporation Transmission lubricant system for an outboard motor
US20220282776A1 (en) * 2021-03-05 2022-09-08 Polaris Industries Inc. Vehicle System

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL7712625A (nl) * 1977-11-16 1979-05-18 Skf Ind Trading & Dev Automatisch variabel drijfwerk met ten minste een over verstelbare riemschijven lopende v-riem.
GB2152164A (en) * 1983-12-29 1985-07-31 Brunswick Corp Bidirectional marine drive lower gear case

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2068885A (en) * 1933-01-14 1937-01-26 Borg Warner Automatic clutch
US2675898A (en) * 1950-09-12 1954-04-20 Connecticut Variable Gear Corp Unidirectional drive coupling
US3762241A (en) * 1972-01-12 1973-10-02 Eaton Corp Drive mechanism
US3901361A (en) * 1974-02-11 1975-08-26 American Challenger Corp Marine forward-reverse clutches with pilot brakes

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2068885A (en) * 1933-01-14 1937-01-26 Borg Warner Automatic clutch
US2675898A (en) * 1950-09-12 1954-04-20 Connecticut Variable Gear Corp Unidirectional drive coupling
US3762241A (en) * 1972-01-12 1973-10-02 Eaton Corp Drive mechanism
US3901361A (en) * 1974-02-11 1975-08-26 American Challenger Corp Marine forward-reverse clutches with pilot brakes

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022308A (en) * 1976-04-23 1977-05-10 Chrysler Corporation Drive coupling and clutches
US4051934A (en) * 1976-04-23 1977-10-04 Chrysler Corporation Bidirectional drive coupling
US4189038A (en) * 1977-07-18 1980-02-19 Chrysler Corporation Drive coupling and clutches
US4138006A (en) * 1977-10-31 1979-02-06 Paragon Gears Incorporated Power transmission of the interleaved, multiple friction plate clutch type
US4244454A (en) * 1979-04-30 1981-01-13 Brunswick Corporation Cone clutch
US5149308A (en) * 1988-08-22 1992-09-22 Kubota, Ltd. Transmission
US20120066975A1 (en) * 2010-08-05 2012-03-22 Asmo Co., Ltd. Clutch, motor and vehicle door opening/closing device
US8484893B2 (en) * 2010-08-05 2013-07-16 Asmo Co., Ltd. Clutch, motor and vehicle door opening/closing device
US20140038478A1 (en) * 2012-01-24 2014-02-06 Arkmos Engineering, LLC Outboard Marine Drive
US10518860B1 (en) 2015-01-26 2019-12-31 Brunswick Corporation Systems and methods for controlling planetary transmission arrangements for marine propulsion devices
US10124874B1 (en) 2015-01-26 2018-11-13 Brunswick Corporation Systems and methods for controlling planetary transmission arrangements for marine propulsion devices
US10696370B1 (en) 2015-01-26 2020-06-30 Brunswick Corporation Systems and methods for controlling planetary transmission arrangements for marine propulsion devices
US9964210B1 (en) 2016-10-31 2018-05-08 Brunswick Corporation Transmission actuator for an outboard motor having a planetary transmission
US10239598B2 (en) 2016-10-31 2019-03-26 Brunswick Corporation Cooling system for an outboard motor having a hydraulic shift mechanism
US10502312B1 (en) 2016-10-31 2019-12-10 Brunswick Corporation Transmission lubricant system for an outboard motor
US9919783B1 (en) 2016-10-31 2018-03-20 Brunswick Corporation Transmission housing for mounting a transmission between a driveshaft housing and a lower gearcase in an outboard motor
US10315747B1 (en) 2016-11-09 2019-06-11 Brunswick Corporation Outboard motors having transmissions with laterally offset input and output driveshafts
US20220282776A1 (en) * 2021-03-05 2022-09-08 Polaris Industries Inc. Vehicle System
US11892067B2 (en) * 2021-03-05 2024-02-06 Polaris Industries Inc. Vehicle system
US12442439B2 (en) 2021-03-05 2025-10-14 Polaris Industries Inc. Vehicle system

Also Published As

Publication number Publication date
IT1066864B (it) 1985-03-12
FR2319051A1 (fr) 1977-02-18
NO147002B (no) 1982-10-04
SE7605285L (sv) 1977-01-24
DE2633056A1 (de) 1977-02-10
BR7603477A (pt) 1977-07-05
NO762565L (en:Method) 1977-01-25
AU503227B2 (en) 1979-08-30
FR2319051B1 (en:Method) 1979-02-16
NO147002C (no) 1983-01-12
NZ180752A (en) 1979-03-16
FI762101A7 (en:Method) 1977-01-24
JPS5224660A (en) 1977-02-24
CA1048426A (en) 1979-02-13
GB1495919A (en) 1977-12-21
AU1372576A (en) 1977-11-10
ES450087A1 (es) 1977-07-16

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AS Assignment

Owner name: FIDELITY UNION TRUST COMPANY, 765 BROAD ST., NEWAR

Free format text: MORTGAGE;ASSIGNOR:CHRYSLER CORPORATION;REEL/FRAME:003832/0358

Effective date: 19810209

Owner name: FIDELITY UNION TRUST COMPANY, TRUSTEE,NEW JERSEY

Free format text: MORTGAGE;ASSIGNOR:CHRYSLER CORPORATION;REEL/FRAME:003832/0358

Effective date: 19810209

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Owner name: CHRYSLER CORPORATION, HIGHLAND PARK, MI 12000 LYNN

Free format text: ASSIGNORS HEREBY REASSIGN, TRANSFER AND RELINQUISH THEIR ENTIRE INTEREST UNDER SAID INVENTIONS AND RELEASE THEIR SECURITY INTEREST.;ASSIGNORS:FIDELITY UNION BANK;ARNEBECK, WILLIAM, INDIVIDUAL TRUSTEE;REEL/FRAME:004063/0604

Effective date: 19820217

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Owner name: CHRYSLER CORPORATION

Free format text: PARTES REASSIGN, TRANSFER AND RELINQUISH THEIR ENTIRE INTEREST UNDER SAID PATENTS ALSO RELEASE THEIR SECURITY INTEREST.;ASSIGNOR:MANUFACTURERS NATIONAL BANK OF DETROIL (CORPORATE TRUSTEE) AND BLACK DONALD E., (INDIVIDUAL TRUSTEE);REEL/FRAME:004355/0154

Effective date: 19840905